EP3961046B1 - Lüfterdämpfungssystem - Google Patents

Lüfterdämpfungssystem

Info

Publication number
EP3961046B1
EP3961046B1 EP20796084.0A EP20796084A EP3961046B1 EP 3961046 B1 EP3961046 B1 EP 3961046B1 EP 20796084 A EP20796084 A EP 20796084A EP 3961046 B1 EP3961046 B1 EP 3961046B1
Authority
EP
European Patent Office
Prior art keywords
fan
resonance structure
sound
frequency
film
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20796084.0A
Other languages
English (en)
French (fr)
Other versions
EP3961046A4 (de
EP3961046A1 (de
Inventor
Shinya Hakuta
Akihiko Ohtsu
Shogo Yamazoe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujifilm Corp
Original Assignee
Fujifilm Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujifilm Corp filed Critical Fujifilm Corp
Publication of EP3961046A1 publication Critical patent/EP3961046A1/de
Publication of EP3961046A4 publication Critical patent/EP3961046A4/de
Application granted granted Critical
Publication of EP3961046B1 publication Critical patent/EP3961046B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/161—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general in systems with fluid flow
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/162—Selection of materials
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/545—Ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a fan silencing system.
  • JP2001-142148A discloses a silencing device for a device comprising a heat source such as a light source lamp unit, and an exhaust fan for exhausting heat from the heat source, in which an air guide member of exhaust air of the exhaust fan is hermetically disposed from an air outflow side of the exhaust fan to the outside of the device, an elastic film body that can vibrate with a sound wave generated by the exhaust fan is disposed on a peripheral wall portion of the air guide member facing a ventilation passage at a position in which the elastic film body at least collides with a flow of the exhaust air and does not block a flow of the air in the exhaust direction, an air chamber is formed on a rear side of the elastic film body.
  • the silencing device disclosed in JP2001-142148A silences a sound by converting sound energy into vibration energy by applying an air flow (wind) generated by the fan to the elastic film body to vibrate the elastic film body.
  • JP2008-036065A discloses an electric blower comprising an impeller having a plurality of blades, an air guide having a plurality of stationary blades disposed around the impeller, an electric motor that drives a rotation shaft to which the impeller is fixed, a substantially cylindrical fan case having an intake port that allows an air flow into the impeller in the center and an exhaust port on a side surface, and fixed to the electric motor in a state of encompassing the impeller and the air guide, a soundproof cylinder having an exhaust port and airtightly fixed to the fan case in a state of encompassing the entire electric motor, a substantially cylindrical silencing unit including a recess portion having a predetermined width and depth on the circumference and provided at a predetermined position on a surface of the electric motor, and a thin film portion having flexibility, which is provided an opening end surface of the recess portion of the silencing unit.
  • JP2001-142148A since a large wind pressure is applied to the elastic film body, a characteristic of the elastic film body is changed in a case in which the air volume and the wind pressure of the fan are changed. Therefore, the characteristic of the elastic film body and a resonance effect formed by a back air layer cannot be used. Therefore, since it is not possible to obtain a large silencing effect aiming at the sound of a specific frequency generated by the rotation of the fan, it is difficult to obtain a large silencing effect on the fan.
  • a resonance type silencer as in JP2008-036065A silences a sound having a single frequency that coincides with the resonance frequency of the resonance type silencer, and has a low silencing effect on sounds in other frequency bands. Therefore, there is a problem that it is difficult to silence the sounds of the plurality of frequencies generated discretely.
  • An object of present invention is to solve the above-described problems in the related art, and to provide a fan silencing system that can silence a sound in a narrow band of a plurality of discrete frequencies generated by a fan while ensuring an air volume of the fan.
  • a fan silencing system that can silence a sound in a narrow band of a plurality of discrete frequencies generated by a fan while ensuring an air volume of the fan.
  • the numerical range represented by “to” means a range including numerical values denoted before and after “to” as a lower limit value and an upper limit value.
  • orthogonal means that it is within a range of less than ⁇ 10° with respect to exact orthogonality, and an error with respect to the exact orthogonality is preferably 3° or less.
  • parallel means that it is within a range of less than ⁇ 10° with respect to an exact angle.
  • a fan silencing system includes a fan, and an acoustic resonance structure, in which the acoustic resonance structure is disposed in a near field region of a sound generated by the fan.
  • the near field region of the sound generated by the fan is a region in which a sound wave is in a near field state.
  • the state in which the sound wave is in the near field is as described below.
  • a propagation direction and an intensity of each sound wave generated from a sound source is determined by a difference of attenuation for each wave number of the wave or space limitation (duct wall, bending of a flow passage, and the like).
  • the sound wave generated from the sound source is not under a control of an influence by the attenuation and limitation described above immediately after the sound wave is generated, and has an amplitude over a wide wave number range including a high wave number component that cannot be propagated to a long distance.
  • the sound wave is propagated over a certain distance or longer, and then becomes a plane wave, and the directionality is determined.
  • the state immediately after the sound wave is generated from the sound source is referred to as a "near field" state. Therefore, a region in the vicinity of the sound source that satisfies the conditions described above is defined as the near field region.
  • the fan which is the sound source in the embodiment of the present invention, generates the sound from a blade portion of the fan, and thus a region at a distance of less than ⁇ /4 from the blade portion of the fan is the near field region. Note that in a case in which the fan is disposed in the flow passage, a region in which a distance from the fan along the flow passage is less than ⁇ /4 is the near field region.
  • a first mechanism of the interaction is as described below.
  • the distance from the sound source is less than ⁇ /4 at the maximum, and thus a phase change of the sound wave due to the propagation is small.
  • the phase of the sound wave is inverted (phase change of ⁇ ) due to the reflection by the acoustic resonance structure. Therefore, since a phase deviation is substantially in a phase inversion state, the sound generated from the sound source and the sound reflected by the acoustic resonance structure and returned to the sound source interfere with each other in opposite phases. Therefore, the two sounds cancel each other out at the sound source position, and the silencing effect occurs at the sound source position.
  • the two mechanisms of the interactions described above are an effect due to the interaction between the sound source (sound wave) and the acoustic resonance structure due to the disposition of the acoustic resonance structure in the near field region. Therefore, since a flow of the wind is irrelevant, it is not necessary to dispose the acoustic resonance structure such that the wind directly hits the acoustic resonance structure. That is, it is not necessary to dispose the acoustic resonance structure to partially block the air duct of the air flow generated by the fan. Therefore, it is possible to silence the sound generated by the fan while ensuring the air volume of the fan.
  • the region in which the distance from the sound source is less than ⁇ /4 is the near field region. Therefore, a size of the near field region differs depending on a wavelength (frequency) of the sound wave.
  • the shaft portion 20 of the rotor 18 has a substantially columnar shape, and one bottom surface side thereof is attached to a rotation shaft of the motor, and the rotor 18 is rotated by the motor.
  • a shape of the blade 22 can be various shapes used in a known axial fan in the related art.
  • the casing 16 fixes the motor, and surrounds the rotor 18 (blade 22) that can be rotated in the radial direction.
  • the thickness of the casing 16 in the rotation axis direction is thicker than the thicknesses of the blade 22 and the shaft portion 20 such that the rotor 18 can be protected from the outside.
  • a thickness of the casing 16 need only be a thickness that can protect the rotor 18 from the outside, suppress the air flow in the radial direction among the air flows generated by the rotation of the rotor 18, and increase the air volume in the rotation axis direction, that is, need only be a thickness about 1.01 times to 3.00 times the thickness of the blade 22 and/or the shaft portion 20.
  • the axial fan 12a may have various configurations of a known axial fan.
  • the film type resonance structure 30a is disposed on a downstream side of the axial fan 12a in a blowing direction.
  • the film type resonance structure 30a is disposed at a position in which blowing by the axial fan 12a (blowing port 16a) is not blocked, specifically, around a region serving as an air duct for the wind blown by the axial fan 12a.
  • the film 34 is disposed in parallel to the rotation axis direction (X direction in Fig. 3 ) of the axial fan 12a, and the film 34 is disposed to face the rotation axis side.
  • the resonance frequency of the acoustic resonance structure is desirably in an audible range (20 Hz to 20000 Hz), and more desirably in a range of 100 Hz to 16000 Hz.
  • the resonance frequency of the film type resonance structure 30a coincide with at least one frequency of the discrete frequency sounds caused by the rotation of the blade of the fan.
  • the silencing effect at the frequency coinciding with the resonance frequency of the acoustic resonance structure can be further improved.
  • the resonance frequency of the acoustic resonance structure coincide with the discrete frequency sound having the largest sound pressure, more specifically, the largest A characteristic sound pressure level among the discrete frequency sounds. As a result, it is possible to effectively silence the discrete frequency sound which contributes greatly to the noise of the fan.
  • the resonance frequency of the acoustic resonance structure coincide with the sound on the lowest frequency side among the plurality of discrete frequency sounds.
  • a general silencing material it is more difficult to silence the lower frequency, and thus the low frequency sound can be selectively silenced by the resonance effect, and then the silencing material can be combined with other silencing materials.
  • the sound in a case of the axial fan, in a case in which the rotation speed is defined as z (rps) and the number of blades is defined as N, the sound (discrete frequency sound) is generated strongly at a frequency of m ⁇ N ⁇ z (Hz) (m is an integer of 1 or more).
  • the resonance frequency of the film type resonance structure is determined by the size (size of the vibration surface, that is, a size of the opening portion of the frame 32), the thickness, the hardness, and the like of the film 34. Therefore, the resonance frequency of the film type resonance structure can be appropriately set by adjusting the size, the thickness, the hardness, and the like of the film 34.
  • the film type resonance structure 30a has the back space 35 on the back side of the film 34. Since the back space 35 is closed, sound absorption occurs due to the interaction between the film vibration and the back space.
  • the film vibration has a frequency band of a fundamental vibration mode and a higher order vibration mode determined by the conditions of the film (thickness, hardness, size, fixing method, and the like), and a determination is made as to which mode of frequency is strongly excited to contribute to sound absorption, by the thickness of the back space and the like.
  • the thickness of the back space is thin, the effect is obtained in which the back space is qualitatively hardened, so that it is easy to excite the higher order vibration mode of the film vibration.
  • the back space 35 of the film type resonance structure 30a is a closed space completely surrounded by the frame 32 and the film 34, but is not limited thereto, and the space need only be substantially divided such that the air flow is inhibited, and an opening may be provided in a part of the film 34 or the frame 32 in addition to the completely closed space.
  • Such a form providing the opening in a part thereof is preferable from the point that a change in the sound absorption characteristic as a gas in the back space is expanded or contracted due to a temperature change, tension is applied to the film 34, and the hardness of the film 34 is changed can be prevented.
  • a density of the film 34 is preferably 10 kg/m 3 to 30000 kg/m 3 , more preferably 100 kg/m 3 to 20000 kg/m 3 , and most preferably 500 kg/m 3 to 10000 kg/m 3 .
  • a thickness (thickness in the direction perpendicular to the surface of the film 34) of the back space 35 is preferably 10 mm or less, more preferably 5 mm or less, and still more preferably 3 mm or less.
  • the shape of the film type resonance structure 30a as viewed from the direction perpendicular to the surface of the film 34, that is the shape of a vibration region of the film 34 is a quadrangular shape, but the present invention is not limited thereto, and the shape thereof may be a circular shape, a polygonal shape such as a triangular shape, an elliptical shape, or the like.
  • the area in which the acoustic resonance structure and the blowing port overlap with each other is preferably 50% or less with respect to the area of the blowing port, more preferably 10% or less, and as shown in Fig. 2 , still more preferably 0%, where the acoustic resonance structure and the blowing port do not overlap with each other.
  • the acoustic resonance structure and the blowing port overlap with each other, it is desirable to have a structure that suppresses the generation of a wind noise while allowing the wind to flow smoothly, for example, by attaching a slope-shaped structure.
  • a surface provided with a vibrating body of the acoustic resonance structure is disposed in parallel to an axis perpendicular to the blowing port of the fan.
  • the film 34 is the vibrating body of the film type resonance structure 30a, and the surface on which the film 34 of the film type resonance structure 30a is disposed is disposed in parallel to the axis perpendicular to the blowing port 16a of the axial fan 12a.
  • the vibration of the film by the air flow generated by the fan hitting the surface provided with the vibrating body of the acoustic resonance structure can be suppressed, and the reduction in the silencing effect due to the wind can be suppressed.
  • the fan silencing system has a configuration in which one film type resonance structure 30a (acoustic resonance structure) is provided, but the present invention is not limited thereto, and a configuration may be adopted in which two or more acoustic resonance structures are provided.
  • a configuration may be adopted in which two film type resonance structures 30a are disposed at a position on the downstream side of the axial fan 12a in the blowing direction such that blowing (blowing port 16a) is not blocked.
  • the two film type resonance structures 30a are disposed such that the film 34 is in parallel to the rotation axis direction of the axial fan 12a, the film 34 faces the rotation axis side, and the surfaces of the two film type resonance structures 30a on the film 34 side face each other.
  • Fig. 5 is a view of the fan silencing system as viewed from the rotation axis direction of the axial fan 12a, and the axial fan 12a is not shown.
  • the film type resonance structure 30a (acoustic resonance structure) may constitute a part of a wall surface (pipe line 26) of the ventilation passage connected to the fan.
  • a configuration can be adopted in which the film type resonance structure 30a is disposed at a position in which blowing (blowing port 16a) is not blocked.
  • the film type resonance structure 30a (acoustic resonance structure) is disposed at a position directly in contact with the axial fan 12a (fan), but the film type resonance structure 30a may be disposed at a position spaced from the fan as long as the film type resonance structure 30a is disposed in the near field region of the sound generated from the fan.
  • a film type resonance structure 30b is disposed at a position spaced from the axial fan 12a, and a pipe line 26 is disposed between the film type resonance structure 30b and the axial fan 12a. That is, in the example shown in Fig. 6 , the pipe line 26 forming the passage of the wind generated by the axial fan 12a is connected to the downstream side of the axial fan 12a, and the film type resonance structure 30b is disposed in an end portion of the pipe line 26 on an outlet side.
  • the acoustic resonance structure be disposed in contact with the fan via an anti-vibration member.
  • a side surface of the frame 32 of the film type resonance structure 30a is in contact with the axial fan 12a via an anti-vibration member 36.
  • the fan silencing system includes a plurality of the acoustic resonance structures
  • a configuration is adopted in which the acoustic resonance structure is disposed only on the downstream side of the fan in the blowing direction of the fan, but the present invention is not limited thereto, and a configuration may be adopted in which the acoustic resonance structure is disposed on the upstream side of the fan, or as in an example shown in Fig. 9 , a configuration may be adopted in which the acoustic resonance structures are disposed on the upstream side and the downstream side of the fan.
  • the acoustic resonance structure can be disposed in the space between the fan and a device case in order to reduce the noise that a human listens.
  • the acoustic resonance structure be disposed at least on the downstream side of the fan, and more preferable that the acoustic resonance structure be disposed on the upstream side and the downstream side of the fan.
  • the resonance frequency of the acoustic resonance structure on the upstream side and the resonance frequency of the acoustic resonance structure on the downstream side may be the same or different.
  • the fan silencing system includes the film type resonance structure 30a as the acoustic resonance structure, and a windbreak member 48 which is disposed to cover the film 34 on the surface of the film 34 which is the vibrating body of the film type resonance structure 30a.
  • the windbreak member 48 is a member that allows the sound to pass through and suppresses the intrusion of the wind. By disposing the windbreak member 48 on the surface of the film 34, it is possible to suppress the film vibration due to the wind pressure applied to the film, which is the vibrating body of the film type resonance structure, by the air flow generated by the fan, and it is possible to suppress reduction in the silencing effect due to the wind.
  • the porous sound absorbing material is not particularly limited, and a well-known porous sound absorbing material can be appropriately used.
  • various well-known porous sound absorbing material can be used such as foam materials and materials containing minute air such as urethane foam, soft urethane foam, wood, ceramic particle sintered material, phenol foam, and the like; fibers and fabric materials such as glass wool, rock wool, microfibers (Thinsulate manufactured by 3M), a floor mat, a carpet, a meltblown nonwoven fabric, a metal nonwoven fabric, a polyester nonwoven fabric, metal wool, felt, an insulation board and a glass nonwoven fabric, and wood wool cement board, nanofiber materials such as silica nanofiber, gypsum board, and the like.
  • foam materials and materials containing minute air such as urethane foam, soft urethane foam, wood, ceramic particle sintered material, phenol foam, and the like
  • fibers and fabric materials such as glass wool, rock wool, microfibers (Thinsulate manufactured by 3M), a
  • the flow resistance of the porous sound absorbing material can be evaluated by measuring a perpendicular incident sound absorbance of the porous sound absorbing material having a thickness of 1 cm and fitting by the Miki model ( J. Acoust. Soc. Jpn., 11(1), pp. 19 to 24 (1990 )). Alternatively, an evaluation may be made according to "ISO 9053".
  • the acoustic resonance structure is the Helmholtz resonance structure 40.
  • the Helmholtz resonance structure 40 includes a frame 42 having a prism shape and an opening portion having a bottom surface formed on one surface, a plate-shaped lid portion 44 having a through-hole 46, which covers the opening surface of the frame 42 on which the opening portion is formed to fix a peripheral portion to the frame42.
  • the Helmholtz resonance structure 40 has a structure in which the air in an inner space 43 surrounded by the frame 42 and the lid portion 44 serves as a spring, the air in the through-hole 46 formed in the lid portion 44 serves as a weight (mass), the mass and spring are resonated, and the sound is absorbed by thermal viscous friction in the vicinity of the wall of the through-hole 46.
  • the lid portion 44 having the through-hole 46 is disposed in parallel to the rotation axis direction of the axial fan 12a, and the lid portion 44 is disposed to face the rotation axis side.
  • the sound of the frequency is silenced by allowing the resonance frequency of the Helmholtz resonance structure to coincide with the frequency of the sound to be silenced. Therefore, there is a problem that the silencing effect is low for the sound of the frequency band other than the resonance frequency, and it is difficult to silence the plurality of discrete frequency sounds generated by the fan.
  • the Helmholtz resonance structure 40 in the near field region of the sound generated by the fan, the two mechanisms of the interaction described above occur, so that the plurality of discrete frequency sounds generated by the fan can be silenced.
  • the resonance frequency of the Helmholtz resonance coincide with any one frequency of the discrete frequency sounds generated by the axial fan 12a.
  • the resonance frequency of Helmholtz resonance is determined by a volume of the inner space surrounded by the frame 42 and the lid portion 44, an area and a length of the through-hole 46, and the like. Therefore, the resonance frequency can be appropriately set by adjusting the volume of the inner space surrounded by the frame 42 and the lid portion 44 of the Helmholtz resonance structure 40, the area of the through-hole 46, the length, and the like.
  • the through-hole 46 is formed in the lid portion 44, but the through-hole 46 may be formed in the frame 42.
  • the outlet/inlet of the through-hole needs to face the direction in which the discrete frequency sound generated by the axial fan 12a is propagated, and in Fig. 11 , the direction of the flow passage of the fan.
  • the Helmholtz resonance structure 40 is provided separately from the frame 42 and the lid portion 44, but the frame 42 and the lid portion 44 may be integrally formed.
  • the air in the through-hole 46 is the vibrating body, and the surface of the lid portion 44 having the through-hole 46 is the surface provided with the vibrating body. Therefore, it is preferable that the surface of the lid portion 44 having the through-hole 46 be disposed in parallel to the axis perpendicular to the blowing port.
  • the windbreak member may be disposed on the surface of the lid portion 44.
  • the shape of the Helmholtz resonance structure 40 as viewed from the direction perpendicular to the surface of the lid portion 44 may be a quadrangular shape, a polygonal shape such as a triangular shape, a circular shape, an elliptical shape, or the like.
  • the fan silencing system includes two Helmholtz resonance structures 40, but a configuration may be adopted in which one Helmholtz resonance structure is provided, or a configuration may be adopted in which three or more Helmholtz resonance structures are provided.
  • the frames of the Helmholtz resonance structure may be integrally formed, or the inner space may be shared.
  • the resonator provided in the silencer may be the air column resonance structure.
  • the resonance occurs by generating a standing wave in a resonance pipe having an opening.
  • the resonance frequency of the air column resonance coincide with any one frequency of the discrete frequency sounds generated by the fan.
  • the resonance frequency of the air column resonance is determined by a length of the resonance pipe and the like. Therefore, the frequency of the resonating sound can be appropriately set by adjusting the depth of the resonance pipe, the size of the opening, and the like.
  • the opening portion in a case in which the opening portion is narrow, the sound wave is reflected at the opening portion and it is difficult for the sound wave to enter the inner space, and thus it is preferable that the opening portion be wide to a certain extent.
  • the length of the short side is preferably 1 mm or more, more preferably 3 mm or more, and still more preferably 5 mm or more.
  • the diameter in the range described above.
  • the film type resonance structure as the acoustic resonance structure from viewpoints of size reduction and thinning.
  • Examples of materials of the film type resonance structure and the frames and the lid portions of the Helmholtz resonance structure and the air column resonance structure include a metal material, a resin material, a reinforced plastic material, a carbon fiber, and the like.
  • Examples of the metal material include metal materials such as aluminum, titanium, magnesium, tungsten, iron, steel, chromium, chromium molybdenum, nichrome molybdenum, copper, alloys thereof, and the like.
  • examples of the resin material include resin materials such as an acrylic resin, polymethyl methacrylate, polycarbonate, polyamide-imide, polyarylate, polyetherimide, polyacetal, polyether ether ketone, polyphenylene sulfide, polysulfone, polyethylene terephthalate, polybutylene terephthalate, polyimide, an acrylonitrile, butadiene, styrene copolymer synthetic resin (ABS resin), polypropylene, triacetyl cellulose, and the like.
  • examples of the reinforced plastic material include carbon fiber reinforced plastics (CFRP), and glass fiber reinforced plastics (GFRP).
  • natural rubber, chloroprene rubber, butyl rubber, ethylene/propylene/diene rubber (EPDM), silicone rubber, and the like, and rubber containing these crosslinked structures are exemplary examples.
  • honeycomb core materials can be used as the frame material. Since the honeycomb core material is lightweight and used as a highly rigid material, ready-made product thereof is easily available.
  • the honeycomb core material made of various materials such as aluminum honeycomb core, FRP honeycomb core, paper honeycomb core (manufactured by Shin Nippon Feather Core Co., Ltd, manufactured by Showa Aircraft Group Co., Ltd., or the like), thermoplastic resin (PP, PET, PE, PC, or the like) honeycomb core (TECCELL manufactured by Gifu Plastic Industry Co., Ltd., or the like).
  • a structure including air that is, a foam material, a hollow material, a porous material, or the like can also be used as the frame material.
  • a closed cell foam material and the like can be used to form the frame.
  • various materials such as closed cell polyurethane, closed cell polystyrene, closed cell polypropylene, closed cell polyethylene, and a closed cell rubber sponge can be selected.
  • the frame material be made of a material having higher heat resistance than the flame retardant material.
  • the heat resistance can be defined, for example, by the time that satisfies each item of Article 108-2 of the Building Standards Law Enforcement Ordinance. In a case in which the time that satisfies each item of Article 108-2 of the Building Standards Law Enforcement Ordinance is 5 minutes or more and less than 10 minutes, it is a flame retardant material, in a case in which the time is 10 minutes or more and less than 20 minutes, it is a semi-incombustible material, and in a case in which the time is 20 minute or more, it is a non-combustible material.
  • the heat resistance is defined for each field. Therefore, the frame material need only be made of a material having the heat resistance equivalent to or higher than the flame retardance defined in the field in response to the field in which the fan silencing system is used.
  • the wall thicknesses of the frame and the lid portion are not particularly limited, and can be set in response to, for example, the size of the opening cross section of the frame.
  • Examples of the film 34 include various metals such as aluminum, titanium, nickel, permalloy, 42 alloy, kovar, nichrome, copper, beryllium, phosphor bronze, brass, nickel silver, tin, zinc, iron, tantalum, niobium, molybdenum, zirconium, gold, silver, platinum, palladium, steel, tungsten, lead, and iridium; and the resin materials such as polyethylene terephthalate (PET), triacetyl cellulose (TAC), polyvinylidene chloride (PVDC), polyethylene (PE), polyvinyl chloride (PVC), polymethylpentene (PMP), cycloolefin polymer (COP), zeonoa, polycarbonate, polyethylene naphthalate (PEN), polypropylene (PP), polystyrene (PS), polyarylate (PAR), aramid, polyphenylene sulfide (PPS), polyether sulfone (PES), nylon
  • a glass material such as thin film glass and a fiber reinforced plastic material such as carbon fiber reinforced plastic (CFRP) and glass fiber reinforced plastic (GFRP) can also be used.
  • CFRP carbon fiber reinforced plastic
  • GFRP glass fiber reinforced plastic
  • natural rubber, chloroprene rubber, butyl rubber, EPDM, and silicone rubber, and rubber having these crosslinked structures can be used. Alternatively, the combination thereof may be used.
  • the surface may be metal-plated from the viewpoint of suppressing rust.
  • the metal material As the material of the film 34 in applications requiring durability.
  • the fan silencing system includes the axial fan 12a as the fan and the noise of the axial fan (propeller fan) is suppressed
  • the present invention is not limited thereto, and a known fan in the related art, such as a sirocco fan, a turbo fan, a centrifugal fan, or a line flow fan, can be applied to the fan.
  • the sirocco fan takes in air from the rotation axis direction of the rotor including blade, supplies the air in the direction perpendicular to the rotation axis, and has the blowing port on the side surface. Therefore, for example, as shown in Fig. 12 , in a case in which the fan is a sirocco fan 12b, the film type resonance structure 30a (acoustic resonance structure) is disposed to be in contact with a blowing port 38.
  • a configuration of the film type resonance structure 30a is the same as the example shown in Fig. 1 and the like.
  • the film type resonance structure 30a is disposed at a position in which the blowing port of the sirocco fan 12b is not blocked.
  • the film 34 is disposed in parallel to the direction perpendicular to the blowing port of the sirocco fan 12b, and the film 34 faces the blowing port side.
  • An axial fan (Model: 109P0612K701 manufactured by SANYO DENKI CO., LTD.) was used as the fan.
  • the axial fan has an outer diameter of 60 mm ⁇ 60 mm and a thickness of 15 mm. Since the casing was attached to the exhaust direction side of the fan, a distance from a front end portion of the blowing port to the rotor blade was about 5 mm.
  • anti-vibration rubber with a thickness of 5 mm was disposed under the fan.
  • the side surface of the casing of the fan was surrounded by acrylic having a thickness of 5 mm.
  • This duct was disposed on the surface of the fan on the blowing port side such that the cross section of the air duct of the fan coincides with the duct.
  • the sound volume was measured by driving the fan by using the produced structure.
  • a microphone 1.27 cm (1/2 inch) microphone 4152 manufactured by ACO, Co, Ltd.) was disposed at a position 200 mm spaced from a center position of the fan in the axial direction at a point offset by 50 mm from a central axis in a horizontal direction and a perpendicular direction in order to avoid an influence of the wind.
  • the microphones were disposed on both an exhaust side and an intake side.
  • the fan was driven by using a regulated DC power supply.
  • a driving condition of the fan was 12 V and 0.25 A.
  • FIG. 14 A horizontal axis of a graph shown in Fig. 14 is a logarithmic display. From Fig. 14 , it was found that a large peak sound (narrow band sound), which is a characteristic of a fan with a rotating blade, appeared at a plurality of frequencies. That is, it was found that discrete frequency sounds were generated. Among them, a large peak had in an integral multiple relationship. In particular, the sound volumes of 1.1 kHz and 2.2 kHz were high.
  • a wind speed at the outlet side end portion of the duct was a wind speed of 3.1 m/s, which was measured by using an anemometer. Hereinafter, a change in the wind speed was not observed until Example 3.
  • a PET film (Lumirror manufactured by TORAY INDUSTRIES, INC.) having a thickness of 75 ⁇ m was attached to the opening surface of the frame with a double-sided tape.
  • the film type resonance structure having an outer shape of 30 mm square, an inner shape of the frame of 24 mm, a PET film thickness of 75 ⁇ m, and a back distance of 6 mm was produced.
  • Fig. 19 shows the measurement results of the sound volume of Comparative Example 3 and in a case in which the portion of the film type resonance structure 30a of Comparative Example 3 was replaced with the duct (simple duct).
  • the film type resonance structure was disposed in the near field region as in Example 1, it was necessary to treat the interaction between the film type resonance structure and the sound source in an integrated manner, and to further consider the interaction with the near field sound of a high wave number that is not propagated to a long distance. In this case, it was considered that the mechanism described above also contributed to a release amount of the sound at a frequency other than the resonance frequency of the film type resonance structure. Therefore, in the near field region, it is possible to obtain the silencing effect with respect to the sound in a wide frequency band.
  • Example 2 By using the same film type resonance structure as in Example 2, a study was performed by changing the peak sound frequency by changing a type of fan.
  • the peak sound could be silenced by the resonance structure in the near field region even at the peak sound frequency of the fan deviating from the resonance frequency of the film type resonance structure.
  • Example 2 the silencing volume of the peak sound, it was found that a case of Example 1 in which the resonance frequency coincides with the peak sound frequency of the fan had a large silencing volume, which was more preferable, than a case in which the resonance frequency deviates from the peak sound frequency of the fan as in Example 2.
  • the design was made by the finite element method by using COMSOL MULTIPHYSICS, so that it was found that the resonance frequency became 1.1 kHz by setting the back distance of the film type resonance structure of Example 1 from 6 mm to 15 mm.
  • An acrylic plate was processed with the laser cutter to produce this film type resonance structure by the same method as in Example 1.
  • the produced film type resonance structure was disposed at a position 30 mm spaced from the surface of the blowing port of the fan.
  • the duct (pipe line) was connected between the film type resonance structure and the fan (see Fig. 6 ).
  • the distance from the center of the film type resonance structure to the sound source portion (blade) of the fan was 50 mm.
  • wavelength/4 at a frequency of 1.1 kHz was 78 mm, it was found that the film type resonance structure was disposed in the near field region.
  • Fig. 21 also shows the measurement results of the sound volume in a case in which the film type resonance structure of Example 3 was replaced with the duct (simple duct).
  • the fan silencing system was produced in the same manner as in Example 1 except that a configuration (see Fig. 8 ) was adopted in which the film type resonance structure produced in Example 3 was disposed on the downstream side of the film type resonance structure of the fan silencing system of Example 1.
  • the silencing effect could be obtained for the plurality of discrete frequency sounds generated by the fan, which are indicated by arrows in Fig. 22 . That is, it was found that the silencing effect could be obtained even at a frequency other than the resonance frequency of the film type resonance structure.
  • Fig. 23 A difference between the two data in Fig. 22 is obtained and shown in Fig. 23 as the silencing volume. It was found that the noise peak of the fan was silenced by 15 dB or more around 1.1 kHz and around 2.2 kHz, and the silencing effect was obtained in other frequency bands as well.
  • the noise level which was noise of 81.9 (dBA) in a case of the simple duct, could be reduced to 74.9 (dBA) in the fan silencing system of Example 4.
  • dBA noise level
  • the noise level has a difference of 3 dBA, a normal person can sufficiently detect the noise, so that the silencing effect at 7 dBA is a level that can be felt to be sufficiently quiet.
  • the film type resonance structure having the same configuration as that of Example 2 was disposed on the exhaust side of the fan. However, the film surface of the film type resonance structure was formed to be lowered by 5 mm to the outer peripheral side (see Fig. 26 ) than in Example 2. The reason of the above is to dispose the windbreak member in Example 6 described below.
  • Fig. 27 shows the measurement results in a case in which the film type resonance structure of Example 5 is replaced with the duct, as Comparative Example 4.
  • the structure lengths in the flow passage direction were both 30 mm, which were equal.
  • Example 5 the air volume of the fan was large and the fan was rotated, and thus the air was nonstationary. Since the wind applied the wind pressure to the film surface, the vibration due to the wind was generated on the film surface.
  • the vibration generated in the film included a wide frequency spectrum, but among them, the resonance phenomenon occurred at a frequency designed as the resonance by the design of the film type resonance structure, that is, a frequency aimed at silencing and around thereof. At this resonance frequency, the vibration generated on the film surface was likely to remain for a long time, and the amplitude thereof was also likely to be amplified in a state in which the fan continues to operate. Therefore, the sound was emitted like a speaker. As described above, it was considered that in a case in which a strong air volume is generated in the immediate vicinity of the fan, the sound was amplified around the resonance frequency, and thus a target silencing effect was hardly obtained.
  • the fan silencing system of Example 5 was produced in the same manner as in Example 5 except that the windbreak member was disposed on the surface of the film including the film type resonance structure (see Fig. 10 ).
  • An urethane sponge (thickness of 5 mm) was used as the windbreak member.
  • the double-sided tape was not used on the surface of the sponge on the film side, and a scotch tape was used on a part of the sponge on the air side surface (position on the lower portion of the sponge, which hits the frame portion of the film type resonance structure) to attach the sponge to the side wall portion of the film type resonance structure to prevent the sponge from deviating from the film type resonance structure.
  • the fan of the produced fan silencing system was driven, and the sound volume was measured on the exhaust side and the intake side in the same manner as in Comparative Example 1.
  • Example 6 the wind speed at the outlet side end portion of Example 6 was measured by using the anemometer. As a result, it was confirmed that the wind speed was 14.5 m/s, and the wind speed was not changed.
  • the fan silencing system was produced in the same manner as in Example 5 except that the Helmholtz resonance structure was used as the acoustic resonance structure.
  • a through-hole length was 3 mm
  • a through-hole diameter was 4 mm
  • an inner space thickness was 12 mm
  • an inner space diameter was 24 mm.
  • the Helmholtz resonance structure was produced by processing an acrylic plate with the laser cutter to have such a configuration.
  • the fan silencing system was produced in the same manner as in Example 5 such that the Helmholtz resonance structure 6 cells constituted a duct wall surface.
  • Fig. 29 shows the measurement results in a case in which the amount of current supplied to the fan is 0.3 A.
  • the measurement results in a case in which the duct of the same length was attached instead of the Helmholtz resonance structure is also shown (Comparative Example 5). The wind speed at this time was 5.5 m/s.
  • the sound volume was measured in the same manner as in Example 7 except that the amount of current supplied to the fan was 1.3 A.
  • the measurement results are shown in Fig. 30 .
  • the measurement results in a case in which the duct of the same length was attached instead of the Helmholtz resonance structure is also shown (Comparative Example 6).
  • the wind speed was 15.1 m/s.
  • a blower 9BMC12P2G001 manufactured by SANYO DENKI CO., LTD. was used.
  • a configuration was adopted in which the fan for the blower was disposed on anti-vibration rubber having a thickness of 10 mm, and the air taken in from the upper portion was discharged in the horizontal direction.
  • the measurement was performed in a state in which the blowing port and the opening portion of the partition 102 were connected by the duct 100 produced by an acrylic plate having a thickness of 5 mm.
  • a schematic view is shown in Fig. 31 .
  • the fan silencing system was produced in the same manner as in Comparative Example 7 except that four film type resonance structures 30a of Example 4 were disposed in a duct shape between the blowing port and the opening portion of the partition 102 (see Fig. 32 ).
  • a distance between the film type resonance structure 30a and the blade of the sirocco fan was 24 mm at minimum, and the film type resonance structure 30a was disposed in the near field region.
  • Example 9 Comparative Example 7, the fan was driven and the sound volume was measured by the microphone MP for measurement.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Claims (12)

  1. Ventilatordämpfungssystem, umfassend:
    einen Ventilator (12a); und
    eine akustische Resonanzstruktur (30a, 30b),
    wobei die akustische Resonanzstruktur (30a, 30b) in einem Nahfeldbereich eines von dem Ventilator (12a) erzeugten Schalls angeordnet ist, wobei der Nahfeldbereich der Bereich von einer Schallquelle bis zu weniger als λ/4 ist, wobei λ eine Wellenlänge einer Resonanzfrequenz der akustischen Resonanzstruktur (30a, 30b) ist, und
    wobei die akustische Resonanzstruktur (30a, 30b) eine Resonanzstruktur des Filmtyps (30a, 30b) ist, die einen Film (34), der einen fixierten Umfangsabschnitt, der so gestützt wird, um eine Filmschwingung zu ermöglichen, und einen Rückraum, der an einer Oberflächenseite des Films gebildet ist, enthält,
    dadurch gekennzeichnet, dass
    das Ventilatordämpfungssystem ferner ein Windschutzelement (48) umfasst,
    wobei das Windschutzelement (48) so angeordnet ist, dass es den Film (34) auf einer Oberfläche des Films (34), die der Schwingungskörper der Resonanzstruktur des Filmtyps (30a) ist, abdeckt, so dass das Windschutzelement (48) einen Schall zu der Oberflächenseite, die mit dem Schwingungskörper der akustischen Resonanzstruktur (30a, 30b) versehen ist, überträgt.
  2. Ventilatordämpfungssystem nach Anspruch 1,
    wobei eine Resonanzfrequenz der akustischen Resonanzstruktur (30a, 30b) mit mindestens einer Frequenz von diskreten Frequenzschallen, die durch eine Drehung einer Schaufel des Ventilators (12a) verursacht werden, zusammenfällt.
  3. Ventilatordämpfungssystem nach Anspruch 1 oder 2,
    wobei, bei Betrachtung aus einer Richtung senkrecht zu einem Blasanschluss des Ventilators (12a), eine Fläche, in der die akustische Resonanzstruktur (30a, 30b) mit dem Blasanschluss überlappt, 50 % oder weniger einer Fläche des Blasanschlusses beträgt.
  4. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 3,
    wobei die akustische Resonanzstruktur (30a, 30b) einen Teil einer Wandfläche eines Belüftungskanals, der mit dem Ventilator (12a) verbunden ist, bildet.
  5. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 4,
    wobei die Oberfläche, die mit dem Schwingungskörper der akustischen Resonanzstruktur (30a, 30b) versehen ist, parallel zu einer Achse senkrecht zu dem Blasanschluss des Ventilators (12a) angeordnet ist.
  6. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 5,
    wobei die akustische Resonanzstruktur (30a, 30b) mit dem Ventilator (12a) in Kontakt steht.
  7. Ventilatordämpfungssystem nach Anspruch 6,
    wobei die akustische Resonanzstruktur (30a, 30b) via ein Antivibrationselement mit dem Ventilator (12a) in Kontakt steht.
  8. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 7,
    wobei mehrere der akustischen Resonanzstrukturen (30a, 30b) mit unterschiedlichen Resonanzfrequenzen vorgesehen sind, und
    die akustische Resonanzstruktur (30a, 30b) mit einer hohen Resonanzfrequenz an einer Position, die näher an dem Ventilator (12a) als die akustische Resonanzstruktur (30a, 30b) mit einer niedrigen Resonanzfrequenz liegt, angeordnet ist.
  9. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 8,
    wobei die akustische Resonanzstruktur (30a, 30b) nur auf einer Stromabwärtsseite des Ventilators (12a) in einer Blasrichtung des Ventilators (12a) angeordnet ist.
  10. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 8,
    wobei die akustische Resonanzstruktur (30a, 30b) auf einer Stromaufwärtsseite und einer Stromabwärtsseite des Ventilators (12a) in einer Blasrichtung des Ventilators (12a) angeordnet ist.
  11. Ventilatordämpfungssystem nach Anspruch 1,
    wobei die Resonanzstruktur des Filmtyps (30a, 30b) ein Durchgangsloch, das den Rückraum mit einer Außenseite kommuniziert, aufweist.
  12. Ventilatordämpfungssystem nach einem der Ansprüche 1 bis 11,
    wobei der Ventilator (12a) ein Axialventilator (12a) ist.
EP20796084.0A 2019-04-24 2020-03-24 Lüfterdämpfungssystem Active EP3961046B1 (de)

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PCT/JP2020/013040 WO2020217819A1 (ja) 2019-04-24 2020-03-24 ファン消音システム

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WO2020080112A1 (ja) * 2018-10-19 2020-04-23 富士フイルム株式会社 音響システム
JP7046238B1 (ja) 2021-01-14 2022-04-01 レノボ・シンガポール・プライベート・リミテッド 電子機器
WO2023032618A1 (ja) * 2021-08-30 2023-03-09 富士フイルム株式会社 通気路用消音器
TWI806407B (zh) 2022-02-08 2023-06-21 宏碁股份有限公司 具散熱和降噪功能之電子系統和相關聲學濾波器
EP4498362A4 (de) * 2022-03-22 2025-07-02 Fujifilm Corp Luftkanal mit schalldämpfer
WO2023181519A1 (ja) * 2022-03-22 2023-09-28 富士フイルム株式会社 消音器付き風路
CN118742951A (zh) 2022-03-22 2024-10-01 富士胶片株式会社 带消音器的风道
WO2024062743A1 (ja) * 2022-09-21 2024-03-28 富士フイルム株式会社 消音器付き風路
JPWO2024070160A1 (de) * 2022-09-28 2024-04-04
KR102840958B1 (ko) * 2023-01-10 2025-08-01 대구대학교 산학협력단 소음기
FR3149053A1 (fr) * 2023-05-24 2024-11-29 Safran Ventilation Systems Dispositif de ventilation ou de compression pour l’industrie aeronautique
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CN113646541B (zh) 2024-03-26
JP2023098879A (ja) 2023-07-11
EP3961046A4 (de) 2022-06-08
JP7804608B2 (ja) 2026-01-22
WO2020217819A1 (ja) 2020-10-29
CN113646541A (zh) 2021-11-12
JPWO2020217819A1 (de) 2020-10-29
EP3961046A1 (de) 2022-03-02

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